Fluid pressure operated clutch



April 1951 J. E.YORTLOFF EI'AL 2,550,373

FLUID PRESSURE OPERATED CLUTCH Filed Aug. 18, 1947 2 Shuets$hqet 1 7O 1 i F; o

INVENTORS d.OP:rL.oF'r-' MLWoonY April 24, 1951 J. E. ORTLOFF ETAL Y FLUID PRESSURE OPERATED CLUTCH 2 Sheets-Sheet 2 Filed Aug; 18, 1947 as as F12. 4-

m mr m Vnm N Q M 4v av AL Y B Av w m 6 Z Y .O e ,AILIEN w w w w 4 6 m 5 u Patented Apr. 24, 1951 UNITED STATES PATENT OFFICE JohnjE. Ortloff and Wa Okla, assignors to Fra poration, Tulsa, Okla.

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yland B. woody -Tulsa nks Manufacturing (10ra corporation of Okla- Application August 18, 1947, SerialNo.769;240

Claims.

This invention relates to a clutch mechanism of the friction plate type and more particularly, butinot by way of limitation, to improvements in an air-controlled clutch actuator mechanism adapted for use withtheclutch mechanism of a rotary draw works of rotary drilling rigs for oil wells.

This invention is an improvement over the A. E. Masek Patent #2,342,880, issued February 29, 1944, and relates generally to an air-controlled actuatormechanism comprising [a cylinder cooperating with a pair of spaced stationary hollow vpiston shafts, and movement relative. thereto to cause simultaneous'movementof a linkage mechanism actuating a pair of friction rings into engagement and disengagement'with a clutch plate for the draw works.

It is an important objectof this invention to provide a clutch mechanism for use on rotary draw works which will substantially eliminate rotating air seals by mounting the actuating cylinder in such a manner to preclude rotation thereof, yet permitting a rotating connection between the actuating cylinder and the clutch mechanism.

And still another object of this invention is to provide an air-controlled actuator for clutch mechanisms which may be easily and positively adjusted for stroke position from an external position of the actuatingcylinder.

And still another-object of this invention is to provide a piston actuating device for clutch mechanisms wherein the piston cups and the packings therefor are only subject to reciprocating motion during engagement and disengagement of the clutch mechanism, and thus eliminating any rotational wear onthecups andpackings tending to cause rapid deterioration and subsequent inefilciency.

And still another object of this invention is to provide an "air-controlled piston actuator for elutchmechanisms wherein-the actuating mechanism is disposed awayfrom the friction surfaces of the clutch mechanism 'and' consequently avoids the friction heat' therefrom.

Andstill anotherobjec't of this invention is to provide an air-controlledactuator for rotary rig clutch mechanismswherein an equalized pressure is provided to the clutch engaging surfaces to insure an efiicien t and-smooth operation of the clutch members and thus elimina'te considerable wearthereof.

.Andstillianotherobjectof this inven'tionzis .to provide :a fluidscontrolled actuator for clutch mechanisms having aslida-blevcylinder co-operats 2 1 ing with rotatingclutch members through the medium of a plurality of clutch dogs adapted to effectively cause engagement-rand disengagement of the clutchingmembers.

And still another object of this inventionis .to provide a fluid-controlled'actuator for clutch mechanisms wherein the exhaust fluid discharging from the actuator is slowedidown or decreased to efiect a shock-absorbing for cushioning of the actuator in one movement thereof causing a disengagementof the clutchmechanism.

Other objects and advantages of the invention will be evident from the following detailed description read in conjunction with the accompanying drawings which illustrate our invention;

"In thedrawings: I

Figure 1 is a front elevational view of the actuator utilized with a clutch mechanism.

Figure 2 is a detailed View in section of the inlet control valve.

Figure 3 is an end view thereof.

Figure 4 is-asectional elevational view showing the actuating mechanism in-tdisengaging relatione ship with the upper portion-of the clutch mechanism.

Figure 5=isa similar view showing theactuator engager mechanism causing engagement'of the clutch mechanism.

Referring to the drawings in detail, reference character 2 indicates a clutch drum which is rotatably mounted through bearings 3-on a stationary shaft 4 'of the draw works of a rotary drilling rig '(not shown). The drum 2 is driven by any suitable means (not shown). The drum is providedwith an outwardlyextending annular edge flange '5. An annular friction plate 6 is disposed parallel to the drum 2 and is provided with friction surfaces 1 and 8 for a purpose as will be hereinafter set forth. The friction plate 6 is secured to the annular flange portion 5 by any suitable bolt means'9 threaded into the-drum flange 5. A pair of driving plates or inner and outer annular rings l0 and I2 are disposed at opposite sides respectively of the friction plate 6. Thefriction plates [-0 and H. are rotatable relativeto the stationary shaft 4 and are adapted to be moved in opposite directions toward each other to engage the friction surfaces J and 8 of the friction plate 6 for engaging the clutch members, and also are adaptedto move away from the friction plate 6 for disengaging the clutch mechanism. The innerfriction ring H! is provided with a plurality of arms l3 circumferentially spaced andextendingforwardly through the group of clutch. plates to a point adjacent the frontface or bearing surface M of the outer driving plate l2.

A clutch dog link |5 is pivotedly connected to the end of each of the arms l3 through pivot pin I6, and its opposite end is pivoted to a link ll through a pivot pin l8, as will be hereinafter set forth. Each of the clutch dog links is provided with a hollow cylinder l9 open at its inner end 20 (not shown) and closed at its outer end 2|. A cylindrical piston 22 is disposed in each of the hollow cylinders |9 and has a rounded outer face 23 adapted to contact the bearing surface M in amanner as will be hereinafter set forth. As clearly shown in Figure l, the cylinders l9 are in communication with each other through a plurality of interconnecting flexible tubes 24 connecting the cylinders IS in series. A cylinder at one end of the series is provided with a fitting 25 permitting the introduction of any suitable pressure fluid into the hollow cylinders l9 to maintain equalized pressure at all points of contact of the pistons 22. A drain cock valve 26 may be provided at the opposite end of the cylinder series in order to adjust or vary the hydraulic ressure maintained throughout the cylinders l9 in a manner similar to the aforementioned Patent #2,342,880. It will be apparent that pressure fluid such as grease, from any suitable source (not shown) may be used in the connecting conduits 24 for each of the cylinders l9.

A substantially circular pillow box 21 is disposed in front of the clutch mechanism and may be. mounted by any suitable bracket support means (not shown). The stationary shaft 4 extends through the pillow box 21, as clearly shown in Figures 4 and 5. Also shown in Figure l, the pillow box is provided with a pair of horizontally spaced hollow piston rods 28 and 29, for a purpose that will be hereinafter set forth. A drive hub 30 is rotatably mounted on the stationary shaft 4' through a bushing 3| by a connection (not shown) with the friction plates. A non-rotatable annular sleeve 38 is disposed on the shaft 4 above drive hub 30 and supports a cylinder 32 acting the hollow piston shafts in a manner as will; be hereinafter set forth. A pin 39 secures the sleeve 38 to the shaft 4. A nut 39' is interposed between the :pill box 21 and the sleeve 38. The outer periphery of the cylinder 32 is provided with spaced peripheral flanges 33 against which are abutting ball bearing members 34 supporting an outer annular race member 35. The race is provided with enlarged bearing portion 36 connecting with the link I! through a pivot pin 31. It will be apparent that the race 35 is rotatable with the rotatable clutch as a piston cylinder for 'drum 2 through the linkage connections as heretofore set out. The cylinder 32 is provided with an annular bore 4|! having an apertured end 4| through which extend the horizontally spaced hollow piston shafts 28 and '29. As shown in Figure 1, the piston shafts 28 and 29 are horizontally spaced 180 degrees apart at substantially opposite sides of the stationary shaft 2. However in Figures 4 and 5, the shafts 28 and 29 are shown disposed in the pillow box 21 at a point above the shaft 4 for purpose of clarification only. The'hollow shafts 28 and 29 extend into the cylinder 32 and each are maintained therein by a suitable packing nut 42 and a lock nut 42 threaded at the opposite end thereof. Any suitable packing 43 is provided to effect a seal of the hydraulic pressure fluid, as Will be hereinafter set forth.

The shafts 28 and 29 act as piston rods where one end thereof is reduced in diameter for receiving a piston cup, piston guide and washer, all of these elements being generally indicated by reference character 44. For purposes of clarity only, the upper half portion of the actuating mechanism, and particularly the cylinder 32 and piston unit 44 are disclosed in Figures 4 and 5. It will be apparentthat the cylinder 32 is annular and extends around the shaft 4 above and below the pillow box, 21. Furthermore, the .piston 44 is substantially doughnut shaped having an inside and outside diameter, and extends in circular path in the annular bore 40. Each of the piston heads 44 for the stationary rods 28 and 29 are disposed in a cylinder 32 which is slidable relative to the pistons on the sleeve 38. The outer race member 35 is provided with any suitable grease oil seal 46. The hollow piston shafts 28 and 29 extending between the pillow box 271 and the cylinder 32 are secured in the pillow box 2? by suitable lock nuts 41 and 48 having packing 49 to effect a leakage seal around the shafts.

A valve unit 45 is interposed in the inlet conduit 50 supplying pressure fluid for the shaft 23 from the source not shown. The inlet conduit 50 is in communication with an annular passageway 5| in the .pillow box 2'! adjacent and surrounding the shaft 28 and communicates with an aperture 53 provided in the shaft 28.

Operation In operation, controlled supply pressure fluid from any suitable source (not shown) is discharged through the valve 45 in a manner as Will be hereinafter set forth. The supply fluid pressure passes around the annulus 5| and through the port 53 into communication with the bore 54 of the hollow shaft 28. The supply fluid pressure flows through the bore 54 and is discharged through a port 55 in the shaft 28 and into the bore 43 of the cylinder 32. The pressure is discharged into the bore 40 behind the piston unit 44 adjacent the piston face 56 as noted in Figure 5. Both ends of the shaft 28 are plugged by any suitable means such as a nut 52. Furthermore the shafts 29 and 29 are secured in a rigid relation with the pillow box 2! by the nuts 47 and 48 and consequently are not movable. The supply pressure fluid discharges into the bore 40 behind the face 56 of the piston 44, and as soon as the pressure builds up in the bore 40, the cylinder 32 and the outside race 35 are caused to be moved horizontally relative to the immovable or stationary piston shaft 28.

As clearly shown in Figure 5, the supply pressure fluid from bore 54 causes movement of the cylinder 32 in a left hand direction according to the Figure 5, which causes a simultaneous movement of the outer race 35 in the same direction to cause movement of the pivot pin 3i to provide a clockwise rotation to the link l1, pivot pin l8 and link l5. The clockwise rotation of the linkage mechanism will bring the plurality of pistons 22 into engagement with the bearing surface M of the outer friction plate |2 causing movement of the outer plate l2 into engagement with the frictional surface 1 of the friction plate 6. The movement of the cylinder 32, above described, will move the center line of the pivot pin 31 to a position slightly past center of the center line of the pivot pin l8, as is clearly shown in Figure 5. The new position of the pivot pin I8 pivoting about the pin l6 forces the piston 22 into engagement with the bearing surface I4. The travel of the cylinder 32 may be adjusted as heretofore mentioned to assure that the pivot pin 31 can be farmers moved tmt hezapproximatezpositionzpasihtheiceirr ter lin'e'rof theapivot pin'i'l'liibyradiustmcn LQ IT shafts 28e-and229laszwil1ibe hereinafter mentioned; Simultaneously: thei liriknihzpiv ing abcutflwn I6 will move the arms l3 in a direction torcause movement on inner :pl'atee hmbQWaaIdLthQ friction p'latext; andteausevengagementi;withithe-:iric+ tional surfacez fli thereof: .Inx;.thisrinfl itiom h actuatormejclianisirrjneluding,thcmistorrArtwork ingzwithatheccylindeni32iand'byi allowing thierpast centerapositionts Of."1pin23"l,"j;has;; caused ithel clutch m'eehanismaindicatedmy :thezplates 8;; ti}. and; M to :be positive'lyceng-agedi:anctcannothe:n ieased-un+ ti1=:theisupp1y pressure fluidi-inz hez ores s "leasedtmexhausted;.and: additina15841912156 pre sureefluidiis directedhtorthe;opposite: faced of the piston tosactuate-the vcylindersManta reverse direction: tocpermitzdisengagement ofuthe; clutch members;

The-outer faceeofzithe xpiston 44ractsasta-1stop for the 'cylihder ?ztmovingrin-saflirectientowards the: pillowrhoxito causerengagementsoftthe clutch membersz. Itawilltbe apparent-that vif any-adjustment zisssdesirede the: stationary; piston.- shafts Zihanda Z roan; hes-moved" or 1 adjustedwbyz -theanuts :Miand: titirelativerto thezcylinder;Handithe bore 4lizto:allowtsuch-iadiustmentr The mov ment of the cylinder is actuated: .by;supply pressure fluid beings present:onaiopncsitmfaces rOfiB and -ET of the:v pistonzdependent1 1113011: the flow throu h a irespectivevhoiloweshaft ZB andy29t=v As 'rahove set iorthether shaft 281 permits F disc'hargewf-iflllideihtq the1100118 ttrforwac tingethe. cylinder 32:;causings-engagemenk of: "the; clutch. memhersz. In: similanmannen:the spaeed hollow shaft;21hise rovidedflwith a iboreatflzcommunieatingiwith'itha controlled? source oh supply; pressure :fluid: (hotashown) 'zfromv inletwconduitifl through anrannulanpassageway 61% and-:portaBZ-r OneJend itan-d directionpase shown in .fii'gure asthercby causing a simultaneous movement of the pivot ipi-n 31 which will move' therlink I! in a counterclockwise-direction; thereby moving the clutch dog link l5 and the cylinder l9 and its co-operating piston 22 away fromthe'bea-ring surface M, to dis- :engagerthe outer plate: l-2:fro1m the friction plate 6. Movement of the link i 5 simultaneously moyes the platez-ltwthroughspivotpin- [Grin-a direction to cause, movement of the inner friction ring it awayifrom the engagementwith the friction-plate 6;therebydisengagingthe'clutch mechanism. As heretofore: set forth; the center line designated at, in: Figure 5 ,,-of pivot pirr 3"l"'-m'oves past-acenter line designated-pot pivot pin F8 to fprOVid an-engaging, positionof the"clutch mechanism: In a disengagement of'the clutch'me'chanismx itwill lie apparentithatthe center line w'iof thepivotipin 3T moves'to the'rightorfrom a past center position relative to the center line 1/ of the pivot pin l8. 7

The valve unit 45, shown in detail in Figures 2 and 3, comprises a housing 65 having threads 66 and 6'! for securing the housing in the intake conduit communicating with the shaft 28. The housing is provided with a bore having a pressure fluid inlet portion 68 communicating with a reduced portion 69 which in turn communicates with a bore 10 of larger diameter. A

flutedipistorr type: valved] iiSIIHIOV'idEdtiD; theibore '10 and: hasxa taperedzpoint L12-: atone .-end= eo-opcrating with a tapered portion 13 of;. the valve bore 10, and acting as a valve seatztherefor. The valve J:lrisasolidsbodysprovided with circumferentially spaced giZOOVesmI flutedrpflrtions 14-fpr purposeeas; will; hes-rhereinafiter set forth; A longitudinal? bore l-fi' isprovidedg intheyvalve" l I. In operation, supplyipressurefluid from theeinlet conduit 5Bi-communicatjes withthe bores 58: and I9:to;mo,v.e the-valve; awayfrom itsseat:13=where- :l 4; and into: the inlet conduit; 50 which in -turn;is inpcommunicationwith thqannular passageway 51rprovideddntherpill b0x=21 to flovvinto the;bore 5:4 ofrshaftarZfi; this mannenthe-valvepermits an uninterrupted flowof supply: pressure fluid: to onet'fa'ce 561- of-tthe cylinder 312; However when supply pressurefluid; is directedfthrough the hollow 'shasftfl29 toathe opposite? face; 51 of-the 1' piston in cylinder 32, causing a reversemovementof the cylinder: 32;ithe; exhaust pressure-in vhorerAifl adjacentithe-face Eli-iszexhaustedithr ough aqportqfifi, borer54 into the: conduit 50.- The} exhaust presisure:willimoverthervalve H against theseatr'lt. However thesmall bore-li'rwill permit a decreased orr'sl'owerr discharge ofqthe exhaust pressure from the bore 54 r of shaft 2.8; A transversely disposed cotter pin LB; or spring; is "provided: in the? valve housingififiat. the rear: of: the valverbody t i in order tolimit its backward travel from input pressure fluid:

In:this= manner, it will: be apparent" that the exhaustspressurerfrom cylinderu3'2 :iSsSlOWG'dydOWIl,

'andpthereforractsaszashock-absorberor:cushiom ing-rz'meansiduri-ng the; movement off-the, cylinder 3:2 causinga disengagement of theclutch-mechae nism'. By using ther valvei'meehanismi 45 itozbleed the: exhaust; pressure and provide azcushion or shock-absorbenfiti will: prevent the:cylinden from moving; in: a reverse?direction at-an: increased momentum, which. might, cause damage topthe piston 44- and other. working: parts This cushioning efiect does not slow-down the-disen- -gagement.u orwreleasei of: the clutch mechanism because theaclutchrisrreleasediasssoon:astthe center line ac of pivot-pin; 3:1: is vagain?movedcpastthe center lineofrv pine late :causera, simultaneous movementnfitheilinkage"mechanismamoving the plates-timandzlzzawayrfrom the platefii A'vvalve peSSure'or -.'force :would; be: required; to: move the Emm the foregoing;- ,it: will; be: apparent that thapresent inventionv contemplates, aclutch mechanism-C having, a hydraulic. actuator, causing engagement; and. disengagement, of the: clutch mechanism. in a positive. and. eflicient manner.

Eurthermora, the actuating. apparatusnis non-rotating relative "tor themotati'ng, clutch mechanism and' as such, eliminates rotating air seals. The

alternate movement of the clutch mechanism by selective supply pressure fluid permits operation of the clutching mechanism in such a manner that the flow of the pressure fluid is unrestricted in the engaging operation, yet the exhaust of the pressure fluid for the engaging operation is decreased or restricted to provide a cushioning action for the release or disengaging operation of the clutch members.

Changes may be made in the specification and drawings without departing from the spirit of the invention within the scope of the following claims, as set forth.

What we claim is:

1. In a clutch mechanism comprising a friction plate and movable inside and outside drivin plates for engagement and disengagement therewith, a hydraulic actuator for the driving plates comprising a movable cylinder, a plurality of clutch dogs pivotedly linked with the outside driving plate and the cylinder, means co-operating with the cylinder to alternately direct supply pressure fluid to the cylinder to cause movement thereof in alternate directions, said pivotable linkage comprising a pair of pivot pins and responsive to movement of the cylinder in one direction to move the center line of one of the said pivot pins past the center line of the other of said pivot pins to move the dogs in a direction to cause engagement of the driving plates with the friction plate.

2. In a clutch mechanism comprising a friction plate and movable driving plates for engagement and disengagement therewith, a hydraulic actuator for the clutch mechanism comprising a movable cylinder, a plurality of piston dogs pivotedly linked with the cylinder and one of the driving plates to cause movement of the driving plates into and out of contact with the friction plate, a plurality of hollow stationary piston rods having a piston flange disposed in the cylinder, means directing supply pressure fluid through one of the rods to one face of the flange to cause movement of the cylinder in one direction, providing engagement of the driving plates with the friction plate, and means directing supply pressure fluid through the other of said rods to the opposite face of the piston flange to cause movement of the cylinder in an opposite direction causing movement of the driving plates away from the friction plate, and valve means interposed in the first mentioned piston rod to cushion the movement of the cylinder in its last mentioned direction.

3. In a clutch mechanism comprising a, friction plate and movable driving plates for engagement and disengagement therewith, a hydraulic actuator for the driving plates comprising a movable cylinder, a plurality of clutch dogs pivotedly linked with one of the driving plates and the cylinder, a stationary piston flange disposed in the cylinder, means directing supply pressure fluid to one face of the piston flange to cause movement of the cylinder in a direction to cause a movement of the clutch dogs with a simultaneous movement of the driving plates into engagement with the friction plate, means directing supply pressure fluid to the opposite face of the piston flange to cause movement of the cylinder in an opposite direction causing a disengagement of the driving plates with the friction plate, and valve means co-operating with the first mentioned means permitting free-flow of supply pressure fluid to the first mentioned face of the piston flange, said'valve means dampening the exhaust of'said pressure fluid from the first mentioned flange face to provide'a cushioning effect to the movement of the :cylinder in the disengaging operation.

4. In combinationwith a clutch mechanism, a hydraulic actuator therefor, and pivotal link members connecting the actuator and clutch mechanism, said actuator comprising 'a, movable cylinder, a plurality of hollow stationary piston rods having a piston flange disposed in the cylinder, means directing supply pressure fluid through the rods toone face of the flange to cause movement of the cylinder in one direction, said pivotal linking mechanism comprising a pair of cooperating pivot pins connected with the cylinder and responsive to the movement of the cylinder in one direction, to move the center line of one of said pivot pins past the center line of the other of said pivot pins to effect an increased locking by the linkage mechanism relative to the clutch mechanism, and means directing supply pressure fluid through the other of said rods to the opposite face of the piston flange to cause movement ofthe cylinder in an'opposite direction to the first mentioned direction for moving the pivot pins in a retrograde movement relative to the center lines thereof.

5. In a hydraulic actuator mechanism adapted to actuate a clutch mechanism having engaging and disengaging plate members, and comprising a movable cylinder, a plurality of hollow stationary piston rods having a piston flange disposed in the movable cylinder, means directing supply pressure fluid through one of said rods to cause slideable movement of the cylinder in one direction, means for directing pressure fluid through the other of said rods to cause slideable movement of the cylinder in an opposite direction, and means includin a valve cooperating with one of said rods to permit a free flow of supply pressure fluid through the first mentioned rod in one direction, said Valve means dampening the exhaust of said pressure fluid through the first mentioned rod in a movement of the cylinder in an opposite direction to the first mentioned direction.

JOHN E. ORTLOFF.

WAYLAND B. WOODY.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 41,586 Wright Feb. 9, 1864 423,333 Medart Mar. 11, 1890 1,844,935 Hinger Feb. 16, 1932 1,865,090 Donovan June 28, 1932 2,039,128 Tiedmann Apr. 28, 1936 2,120,798 Criley June 14, 1938 2,342,880 Masek Feb. 29, 1944 2,388,857 Lindsley Nov. 13, 1945 

